Rotary engine



' Sept. 16, 1958 G. E. MALLlNcKRoDT 2,851,998

ROTARY ENGINE 4 Sheets-Sheet 1 IFiled Dec. 5, 1956 \\k N ,y f \\\\\1 ms QUI @E s i 1 mm n lilil @il mi Ll w l @.QT A. a m E M jmw/m mm n Vl|}\1V m. m t m 1\ M., n@ l l w m mv mv mv h l.'

Sept. 16, 1958 G. E.- MALLINCKRODT ROTARY ENGINE 4 Sheets-Sheet Filed Dec. 3, 1956 Sept 16, 1958 G. E. MALLlNcKRoDT '2,851,998

ROTARY ENGINE 4 Sheets-Sheet 5 Filed Dec. I5, 1956 sept. 1s, 195s Filed Dec. `I5, 1956 G. E. MALLINCKRODT ROTARY ENGINE 4 Sheets-Sheet 4 United States Patent O ROTARY ENGINE George E. Mallinckrodt, St. Louis, Mo., assignor to Elliot Enterprises, Incorporated, St. Louis, Mo., a corporation of Missouri Application December 3, 1956, Serial No. 625,978

17 Claims. (Cl. 121-49) This invention relates to rotary engines of the type in` which several rotating systems (having alternating pistons) interchange angular momentums during certain reverse-locking events, and between which systems certain expansion events cause the systems to overrun one another alternately to supply power to a shaft through power integration means.

Among the several objects of the invention may be noted the provision of means for producing in a greater range of engine sizes reliable interchange of piston positions during reverse-locking events preparatory to expansion events; the provision of means of the class described which is hydraulic in character, being adapted for compact design, self-lubrication and trouble-free mechanical operation; the provision in such apparatus of a hydraulic collision process for assisting and controlling a gaseous collision process in transferring momentum from one rotating system to the other, whereby thermodynamic operation may be improved; and the provision of Vsmooth and stable performance characteristics in machines of this class. Other objects and features will be in part apparent and in part pointed out hereinafter.

The invention accordingly comprises the elements and I combinations of elements, features of construction, and arrangements of parts which will be exemplified in the structures hereinafter described, and the scope of which will be indicated in the following claims.

In the accompanying drawings, in which one of various possible embodiments of the invention is illustrated,

Fig. l is a partial longitudinal jogged section of an engine embodying the invention, being taken on line 1-1 of Fig. 2, some of the parts at the left which are the same as p-arts shown at the right, being omitted;

Fig. 2 is a cross section, taken on line 2-2 of Fig. l, the engine being shown in an intermediate position of parts;

Fig. 3 is a cross section taken on line 3-3 of Fig. 1;

Fig. 4 is a developed view of section 4--4 of Fig. 2;

Fig. 5 is a developed view of section 5-5 of Fig. 2;k

Fig. 6 is a skeleton diagram of parts 'corresponding to their neutral positions shown in Fig. 2, wherein one rotor is advancing upon the other rotor, the latter being reverse locked; Y v Y Fig. 7 is a view similar to Fig. 6, showing further advance of the one rotor relative to the reverse-locked rotor;

Fig. 8 is a view similar to Fig. 7 but showing further 4advance of the one rotor and retreat of the other from reverse-locked position; and, f Fig. 9 is a view of a position of parts simil-ar to Fig.

6, except that the rotor positions have been interchanged.

The stippling shown in Figs. 1, 2 and 6-9 is arbitrary and for the purpose of diagrammatically distinguishing one connected set of pistons A, B, C, D, L, M and grooves P, Q on rotor 31 from an unstippled set ofconnected pistons W, X, Y, Z, N, O and grooves R, S on rotor "ice Indiagrammatic Figs. 6-9 the unstippled pistons W, X, Y, Z, N, O and grooves R, S on rotor 29 are dotted as a further distinction.

Corresponding reference characters indicate corresponding parts throughout'the several views of the drawings.

Referring now more particularly to Fig. 1, there is shown at numeral 1 a stationary ring to which cylinder heads 3 and 5 are attached by means of through bolts 8. Parts 1, 3 and 5 form an annular or toroidal cylinder generally numbered 7. The ring 1 is provided with a jacket 9 to form a water-cooling space 11. The cylinder heads 3 and 5 are formed with necks 13 and 15, respectively, in which are press-fitted, angularly iixed flanged liners 17 and 19, respectively, held in proper axial press-fitted positions by adjusting nuts 21 and 23, respectively threaded to the necks 13 and 15. The flanges ofthe liners are numbered 25 and 27, respectively, their inside faces being xed and substantially Hush with the inside faces of the cylinder heads 3 and 5.

Located between the flanged portions 25 and 27 are abutting rotors 29 and 31. These have hollow quills 33 and 35, respectively, extending through and out from said liners 17 and 19. Within'the quills 33 and 35 are bearing sleeves 37 and 39, on a power shaft 41 extending axially through the machine. These sleeves 37 and 39 form bearings for the rotor quills 33 and 35, respectively.

Carried on the rotor 31 and extending in an axial direction over the outside of the rotor 29 are power pistons A, B, C and D (Fig. 2). Carried on the rotor 29 and extending in an axial direction over the outside of the rotor 31 are power pistons W, X, Y and Z. The power pistons A, B, C, D on rotor 31 interdigitate with the power pistons W, X, Y, Z on rotor 29 and all of them are within the annular cylinder 7. rRing sealing means 2 are employed in each piston, the details of which are of no concern to the essentials of the present invention and they are therefore shown diagrammatically by hatching. Thus power cylinder 7 is formed on the outside by the ring 1, on 'the ends by the heads 3 and 5, and on the inside by the circular portions of the rotors 29 and 31 that lie just within their pistons.

In the heads 5 are provided inlet ports I and exhaust ports E. Conventional fuel carbureting means such as a carburetor or fuel injector (not shown) is connected with the inlet ports I. Ignition means, countersunk in the head 3, are shown at G, preferably of the continuous, so-called glow-type, having a conventional exciting circuit requiring no electrical timing means. If, as may be, a spark-type ignition is used, then suitable timing will be required in the exciting circuit. The glow type is employed for purposes of description.

Fastened to the cylinder heads 3 and 5, respectively, are Vsupporting frameworks 43 and 45, supporting inwardly directed cam tracks 47 and 49, respectively. The following description of reverse-locking parts operative with cam track 49 on the right-hand end of the machine (Fig. l) is identical with the description applicable to the reverse-locking parts operative with cam track 47 on the 'left-hand end of the machine, The numbering of these parts will therefore: be identical and the one description will apply to both sets of such parts. As will be seen from Fig. 1, some of the parts at the left-hand end of the machine are not shown, in order that the scale of Fig. 1 may be as large as possiblein the space available; but it will be understood that the parts not shown at the left-hand end of the machine are the same in form and operation as those shown on the right-hand side.

Referring then to the right-hand side of the machine as shown in Fig. l, quill 35 of the rotor 31 has attached thereto a hub 51. The corresponding hub S1 at the left-hand end of the machine is attached to quill 33 of sleeve 87 is` splitand provided with a nut 91.

@senese rotor 29. Lock nuts 53 are used for such purposes. Extending from each hub S1 are lugs 55, in which are rotary pintles 57. Clamped to each pintle 57 is an L,shaped follower link 59,one arm of. which (Fig 3.,) is split, as shown at 61 and providedl withA a clamping bolt 63 for clamping each arm fast toits, pintle.. At the end of the. otherarm of,each.follower linhSS.. is a roller follower 65 engageable, with. cam.. track, 49. Springs 67 maintain engagement. between. the; follower rollers 65 and thev camtrackti.. Each spring` 6.7. has a bail 69 engaging its respective lugrSS and anchors 71 on the, en dsof1 itsrespectiye p intle 5,7, and iswound with tensionV in the appropriate direction toz effect said engagernent.V

The4 camV track 49, for the number (eight) of'power pistons shown,l is o generally square form, having four tljats 73, joined by four corner fillets 7S. This arrangement permitsfree rotation of the respective hub 51' with its lugs 55-in one direction (clockwise in Fig. 3, as shown by the curved dart F'). When the parts are. in or near the positions shown in Fig. 4,' reverse rotation isy prevented; This is referred to herein as a reverse-locked position. The reason for the reverse-locking eiiect is that, each compression thrust H is quite close to a perpendicular position relative to its respective ilatv 73 at a pointadjacent its respective fillet 7S. This, in view of the tension wound into its respective spring 67, will notr allow anticlockwise rotation of the respective fol'- lower link 59. It is to be understood that there is a small; range of positions' nearperpendicularity of; the vectorsH within which range reverseA locking canoccur. Thisobviates a harsh irnpact'esectd upon reverse locking, resultingY in what may bedesignated' a soft reverselocking-actiom which is' conducive tolong roller and' cam track life. The stated range is measured' byY onlyY a few degrees.

Duringy clockwise rotation of thefrespective hub 51' and lugs (Fig. 3l), the followerr links oscillate inV and out around their pi'ntlesY 57' as thev rollerfollowers 65 traversethe cam; It will' be understood that, although Fig. 3-showsthe reverse-locking cam andfoll'ower arrangement on the right-'hand' end of` the machine, the

one on the left-hand endinvolvingcam track 47'- is the same in form` and? the carnV tracks:v 47 and- 49l are in the same positions relative to the variousVv parts; ofL cylinder 7. Sincethe respective=liubs S1 are attached to the respective quillsv 35 and' 33'lof the respective rotors 31 and 29, the rotors, andV their attached power pistons (A, B, C, D) and (W, X, Y, Z)v respectively have certain reverse-locking positions: The reverse-locking position for rotor 31 is shown in Figs; 2; 6 andIT;-thatf'or rotor 29 in Fig. 9. The direction oftreerrotations; for both rotors will accord to downward piston movements at the top of Fig. l and upward pistonr movements at the bottom. This corresponds to clockwise movement; in Fig. 3 and anticlockwise movement in. Fig'. 2: rElie reverse-locking direction is anticlockwise in Fig. 3 and'clockwisein Fig. 2.

Bolted to each hub 51; (see bolts 77) isfa spacer ring 81 and a ywheel 79.V The-bolts also hold@ the angeszSS of inner and outer anchoringV sleevesA S5 and 87 for clamping one end of a helical drive spring 89. The outer When the nut 91 is run in on the sleeve 87', one end'of the spring 89 is gripped. Thel other end'o the spring 89 is anchored between sleeves 93"k and 9 5; the outer onefof which is also split for reception of a nut 97`for gripping purposes. The right-hand ends 991 ofthe anchoring sleeves 93 and 95 are pinned` to. the shaft: 41 (see= p in 4 only partly shown in Fig. l. Thus rotor 31 is connected at the right to shaft 41 through one spring 89 shown in Fig. l, and is connected at the left to shaft 41 through another spring 89 which does not appear in Fig. l, but is identical to the spring 89 and its connections as shown and described.

Reverting to the central portion of the machine near section line 2-2 of Fig. 1, and to Fig, 2, numerals 109 and 111 indicate liner rings attached within the rotors 29 and-31, respectively'. As shownin Fig. l, the abutting ends of-therotors 29 and 31 are cup-shaped andtogether form a circular cavity within the liners. This cavity surrounds; the shaftl 41 and isgenerally numbered 65. In this cavity 6 are four control pistons, two oi" which (marked-L, M) are bolted to therbottom of the cavity part in rotor 31 carrying power pistons A, B, C, D, and the other two of which (marked N, O) are bolted to the bottom of thecavity part in rotor 29 carrying power pistonsW, X, Y; Z1'. All oi the bolts 4for fastening these are not shown, but invFig. l the positions of certain,A of thebolts 4` are indicated by dotted lines rotated intoV the plane of the section. It will be noted thatV only one control piston L on rotor 31 and one control piston N on rotor '29 appear in Fig. l (see jogged section line I-l on Fig. 2), whereas all of the control pistons L, M, N, O appear in Fig; 2 (see sectionV line 2-2 on Fig. l). Fig. 2 also shows-only some of the bolts 4 used, the remainder bei'ngomittedJ to avoid confusion in the drawings.

- Allvof the pistons on rotor 31 (Figl) areA arbitrarily stippledfvfor-emphasig thoseonrotorv 29 are not. For the samerreason, in`Figs. 6-9`the pistons-on rotor 31 are shownsol-idL and those onrotor29 are dotted.

I'nfthe bottomrof' the cavitywithin theaend of rotor3-1 no t occupied by the pistons: L, M are symmetrically locatedsector-shaped grooves P, Q(Figs. 2, 4 and 6 9). Thesef. are.. also stippled where exposed, to emphasize that theyrrotate.- with pistonsA, B, C, D, L and M. In the bottonr off the Vcavity within theend of rotor 29 not oc- Quped vby pistons NandO, are. symmetrically locatedv sector-shaped grooves; R,Y S. These grooves R, S are not stippledbutaare shownby dotted;i lines in Figs: 6-9 to indicate. that. they rotatewith pistons, W, X, Y, Z, N and O.` These also show inFig. 5- in solidlines. The ggoovesP andQshow in Eig. 2, butthe grooves RandS, being above the planeeof thisllatter section, do not appear. None otthegrooves R, S.. P or Q appear in solid lines in the Fig..,l,axial section, but dottedrepresentations of P and R have. been rotated into the plane of this section for clarifyingtheir. radial, positions.

As abovedescribed, thetlangesZgS. and 27 of liners 17 and 19` are axed, to thecylinder headsA 3 and 5 andare therefore stationary.v In ange 2 7 are located four short arcuate grooves J-1, 1 2, J'-3.and,li4 (see Figs. 2, 4 and 6"`9). These (as indicatedv in Fig. 4) become connected at certain times with the inside of the cavity by means of holes 113, drilled through the radialV part of the rotor 31 that forms; one end of the. cavity 6. The holes 113-con nectpermanently respectively with passages 115 'in the pistonsL' andM, which arebolted to the rotor 31. The members of-eachl pair ofA passages 115 respectivelyA extend tothe'opposite face ofthel piston L or M,vas the case may be. For convenience in manufacture, passages 1f1'5areright-angular grooves cutvv into-the outer peripheriesof l@the pistons.

v In the other ange 25, are located four short arcuate grooves- K-'1',.K,2,` K-3- and vK-4 (see Figs. 5'9. These as shown in Fig. 5; are connected' at.certain times with the, inside of. the cavity 6 by'means of `holes 117, drilled through theradial part of the rotor 29. that forms the other end'ofj the cavity. The holes 117 respectively connect permanently with passages 119 in theI control pistons Nand O, which are bolted to the rotor 29. The members'of each pair' of passages 119 respectively extend to the oppositeV face ofthe piston N or O; as the case may be; For manufacturingcorrvenience, these-passages'1'19 are also right-angular grooves cut into the outer peripheries of the pistons.

In Fig. l, groove 1 1, one hole 113 and one passage 115 have been rotated into the plane of the Fig. 1 section and shown in dotted lines. Also in Fig. l, groove K-1, one hole 117 and one passage 119 have been rotated into the plane of the Fig. l section and shown in dotted lines. This is for the purpose of showing the relative axial positions of these parts. Figs. 2 and 6-9 will show their relative angular positions in connection with the description to be given. The developed views of Figs. 4 and 5 are illustrative details of them.

Referring to Figs. 2-9, operation is as follows, keeping in mind that the rotary directional dart F of Fig. 3 will appear in the reverse direction as shown in Figs. 2 and 6-9:

Starting with the parts as shown in Figs. 2 and 6 (the latter being diagrammatic), the rotor 31 carrying pistons A, B, C, D, L, M is taken to be in reverse-locked position (see the reverse-locked position of the followers 59, 65 on the cam track 49 in Fig. 3). An expansion (explosion) event is occurring both between pistons A and W and between pistons C and Y. An exhaust event is occurring both between pistons W and B and between pistons Y and D. A suction or fuel injection event is occurring both between pistons B and X and between pistons D and Z. A compression event is occurring both between pistons Z and A and between pistons X and C. The control pistons L, M ou rotor 31 are in symmetrical bisecting positions over the respective grooves R and S in rotor 29 (Fig. 6), providing free communication from front to rear of each piston. The control pistons N and O on rotor 29 are in symmetrical bisecting positions over the respective grooves P and Q in rotor 31, also providing free communication from front to rear of these pistons respectively. The passages 115 of control piston L are stationary and through holes 113 are registered with stationary groove J-l, thereby affording an auxiliary restricted fluid communication from one side to the other of piston L. The passages 115 in stationary control piston M are registered through holes 113 with the stationary groove J-3, forming an auxiliary restricted communication from one side to the other of the piston M. The stationary grooves J2 and I-4 are not at this time in registry with any other passages. None of the stationary grooves K-l, K-2, K-3, K-4 is in registry with any of the passages 119 in pistons N and O.

Assuming now that the'rotor 29 advances anticlockwise from the Fig. 6 to the Fig. 7 position, further gaseous compression (or gaseous collision) occurs between pistons Z and A and between pistons X and C, rotor 31 with its pistons A, B, C, D, L, M being reverse-locked under reaction from the expansion occurring between pistons A and W on the one hand, and Y and C on the other hand. During this action, the hydraulic-control pistons O and N advance upon stationary control pistons L and M, respectively, thus squeezing hydraulic uid from front to rear of the pistons N and O, respectively, through the grooves P, Q, R and S. Fluid is also forced past pistons L and M via ports 115, 113, I-l and 115, 113, J-3 respectively. Since the fronts of the pistons N and O are approaching the anticlockwise ends of the grooves P and Q respectively, increased throttling of flow occurs from fronts to rears of pistons N, O, so that in addition to the gaseous collision process occurring between pistons Z and A and between X and C, there will occur an increasingly forceful hydraulic collision process between the control pistons N and M on the one hand, and between O and L on the other hand. Thus the gaseous collision process going on in the power cylinder 7 is assisted by the hydraulic collision process in the control cavity between rotors 29 'and 31.

The next step in the process will be seen by comparing Figs. 7 and 8. In proceeding from Fig. 7 to Fig. 8, the rotor 29 continues to move and the sum of the said gaseous collision and hydraulic collision processes causes angular momentum to be transferred from the rotating system connected with rotor 29 to that connected with rotor 31, and ultimately moving the latter from its reverse-locked position. 'I'his moves pistons A, B, C, D, L and M as indicated in Fig. 8. But during the rst part of this operation the rotor 29 is still overtaking the rotor 31 as the parts tirst approach the Fig. 8 coniguration but this does not continue for long. However, as this overtaking process proceeds from the Fig. 7 configuration to the Fig. 8 configuration, the passages 115, 113 associated with pistons L and M, respectively, get out of register with respect to the grooves I-l, J-3, respectively, so that the remaining charge of hydraulic Huid between pistons O and L on the one hand, and between pistons N and M on the other hand, becomes completely trapped. The result is a substantially inelastic connection between the rotors 29 and 31 which carries them together in an anticlockwise direction during the action as depicted in Fig. 8. The two rotor systems then move as one system, with all of the angular momentum that was in the system connected with rotor 29, divided between the systems connected to 29 and 31. The result is that (Fig. 8) both move with the same langular velocity equal to half the maximum velocity of the rotor 29, the moments of inertia of both systems being the same, since their structures are identical.

In the Fig. 8 configuration, the rotor 29 is moving into the range of reverse-locking activity of its reverse-locking elements 59, 65, and ultimately moves up to the reverse.- locking position such as shown in Fig. 9. By this time, as shown in Fig. 8, the ignition devices have been exposed to the compressed charges in the clearance spaces between pistons Z and A and X and C, respectively, thus having ignited them for expansion by the time pistons Z and X arrive at their nal reverse-locked positions, as shown in Fig. 9. This second expansion event initiates a second cycle.

Thus it will be seen that in Fig. 9 the rotor 29 has moved into reverse-locked position wherein its pistons Z and X cover the ignition devices G, and the expansion event which proceeds between pistons Z and A and between X and C places the rotor 31 in the position that rotor 29 had initially in the Fig. 6 conguration. It will also be noted that the passages 119, 117 associated with control pistons O and N, respectively, have come into registry with the stationary grooves K-l and K-3, respectively. This has the effect of connecting the spaces on opposite sides of the control pistons O and N on rotor 29 when reverse locked. Also, the control pistons .L and M on rotor 31 are in bisecting positions over grooves R and S, respectively, which form uid passages from the fronts to rears of these pistons L and M. Thus is broken the temporary inelastic hydraulic connection between rotors which assured that the overtaking rotor 29 would enter the reverse-locking range in displacing the reverse-locked rotor 31.

The above has described a sequence of events requiring 45 of motion of each of the rotors 29 and 31. This resulted in interchange of the rotor positions (compare Figs. 6 and 9). The, machine is then as in Fig. 9.

The operation for the second cycle is similar to that of the operation above given for the irst cycle, except that the relations of movements of the power pistons AB, C, D and W, X, Y, Z are interchanged; likewise, the movements between the control pistons L and M and grooves R and S on the one hand, and the movements between the control pistons O and N and the grooves P and Q on the other hand are interchanged. Nevertheless, the actions on the power events in power cylinder 7 by the -control events in the cavity 6 are the same. For example, consider in Fig. 9 that the rotor 31 (pistons A, B, C, D) will advance on rotor 29 (pistons W, X, Y, Z). This advances control piston M toward the stationary control pistonO, and at the same time moves the groove Q ,anticlockwiseunder the piston O. Thus. duid is squeezed frombetween control pistons M and O into location b etweentpiston O and receding piston` L. This, forv example, at'rst occurs-through thegroove Q, Ybut gradually the entry end ofl this groove Q isbeing throttled as it moves under piston O. This gradually shuts off the flow, so-as to provide the increasing hydraulic: collision assistance` to the gaseous collision event occurring between power` pistons D and Z. At the; time of shut-ott of this flow throughY groove Q, hydraulic ilow will voccur past control piston O through its passages 119, 117 and registered groove K4. Ultimately, as rotor 29 again moves, passages 119, 117 in piston O leave groovev K-l and the two rotors 29,31 move inv inelastic `hydraulic connection with one: another untilpassages 115, 113-V of piston M register with groove-1 4, whereupony this connection is broken and rotor'29 released from rotor 31. as the latter again reachesk a position within-its reverse-locking range.

Summarizing the operation, eight power cycles 'occur for eachrevolution of the power shaft. The first, third, fifth and seventh cycles operate by overrunning action of the pistons and porting grooves connected with rotor 29'with respect to the pistons and porting grooves connected with stationary rotor 31; and the second, fourth, sixth and eighth cycles operate with similar results by overrunning action of the pistons and po-rtin-g grooves connected with rotor 31 with respect to the pistons and porting grooves connected with stationary rotor 29. During the first, third, tifth and seventh` cycles, the passages 115, 113 of pistons L and M cocperatewith stationary grooves 1-1, 1.2, 1-3 and 1 4. During the second, fourth, sixth. and eighth cycles, the passages 119, 117 of pistons N and O cooperate with stationary grooves K-1, K-Z, K-3 and K-4.

It willbe understood that the reverse-locking parts, including 55, 59 and 65, as shown in Fig. 3 for rotor 31 are duplicated on rotor 29 at the. other endof. the machine, but not shown. In the latter casev the reverselocking parts corresponding to: parts 59 and 65 have the same structural relationship to pistons W, X, Y, Z on rotor 29 as the parts 5 and 65'haverelative to pistons A, B, C, D on rotor 31.

As each rotor is intermittently driven under, an expansion event and moves itsV follower system 51, 55, 57, 59, 65 along with its. ywheel 79, it drives the shaft 411 by winding up its respective. connecting spring 89, the

other spring 39 connecting the other'` rotor system with i the shaft unwinding. The springs therefore form means whereby alternately energy is delivered. from the respective rotors to the common shaft 41 and permit alternate overrunning of one rotor with respect to the other. In eiect they integrate energy at the shaft received alter- `nately from the rotors.

The cavity between rotors 29 and 31 is filled with a hydraulic iluid lubricant, which may be subject to leakage. Inlet supply ports into the cavity 6 between rotors for hydraulic fluid are shown at numerals 121 on rotor 31 in Figs. l and 2. Corresponding outlet openings 127 are provided in rotor 29. The radial positions of openings 121, 127 are shown inV Fig. l by rotation of one each into the plane of the section. All of the openings 121 are supplied from a groove 123 around the quill 35, an inlet connection for this groove bein-g shown at 125; All of openings 127 are connected to a groove 129 having an outlet 131. By carrying a suitable pressure head `on the inlet 125, circulation may be elected and loss of lubricant from the cavity between rotors 29 and 31 may be made up.

Itwillbe understood. that while various grooves have beenreferred to as forming certain passages, slots, cored ordrilled holes and the like may be used, and these are therefore to be considered as equivalents. It is also to be'noted that the type of rotary engine to which the inventionvk applies is sometimes referred to. in the art as an alternating piston engine, meaning that groups of interdigitatingzpower pistons. on-.rotors infatoroidalzor. annular cylinder move alternately in carrying, out; thermo-- dynamiccyclicprocesses.. Inthe same sense, the groups ofY control pistons L M and NO described-hereiniare` to be considered as interdigitating. in theA cavity. 6- and being. of. the alternating type. r[he term alternatingis: alsov used. in thev sense. that the pistons off oneV rotor alternate in. positiony With-respect to the pistonson; the other rotor. Thisis also true of'certain passages such as the grooves P, Q, R, S.. lnl the case of' grooves 1'-1, 1-2, 1 3, Lf-- an K-L K Z; K-3,. K.4, the members of the respective groups alternate-in position, peripherally considered. n

WhileA the-passages119, 1:17 (through pistonsN and O') and' the passages 1115*; 113' (through pistons'L and1M') are shown as grooves on the piston peripheries, it will-be understood that these may-be in the form of drilledor coredpassages-from one wall=to another of the respective pistons; Also, whiielthe grooves P and Qfin rotorf 31 and the grooves R and-S-inrotor 29 are shown as open throughout'their lengths, it will be understood that these also' may be cored'passageswith-open ends. The same is true'of the grooves 1-1, 1-2, 1 3: and 1 4, and K-l', K-Z, K-S and K-4. In thisrespect'the terms grooves, holes, ports, slotsl and thev like are to be considered as synonymous.

The engine'above described is of the so-called unidirectional free piston variety inA the sense that the motion of the cooperating pistons relative to one another has no positive: constraint' through any mechanical linkage. It will' be observed; on the' other hand', that the rotary systems to which the power pistons are attached carry controlrneans in theforms of the pistonsy L, M, N, O which' are adapted to be locked. for equal movements thereof and of the rotary" systems during a portion of the gas-buffered collision'k event that occurs during gas compression between the power pistons. Timing means for locking iseffected byv the hydraulic porting, which is controlldby the relative motions between the rotary systems and between them and the frame.

Inview of,`r the above, it will be seen that the several objectsl of.` the invention are achieved and other advantageous results attained.

As. various` changescould be made in the above constructions'without` departing from. the scope of they invention, it is intended that` all matter contained' in theabove descriptiorrorshownin the accompanying drawings shall be interpreted'.as illustrative and not-in a. limiting sense.

I claimz.

1; Rotary apparatus comprising an assembly ofa stationary support for an 'annular cylinder and at Vleast two cooperating rotary systems, having interdigitated power .pistons insaid. cylinder, wherein alternately each system advances upon the other to effect a gas-'buttered collision event between said power pistons, said rotary systems also including interdigitated control pistons in ya liquid medium located in acavity formed by the rotary systems, and fluidporting meansV arranged between the stationary support, the rotary systems and the control pistons, adapted upon movements between the rot-ary systems relative to each other and the support, irst to produce Ia liquid-buffered collision event between the control pistons during a. gas-buffered collision event between the power pistons, whereby the latter event is, assisted by the former event in partially transferring momentum from one rotary system to the other, second to close whereby the rotary systems move together in a substantially inelastic relationship without substantial transfer of momentum between them, Iand third to reopen and releaser one rotary system from the other duringan expansion event `and substantial'completion of momentum transfer.

2. Rotary apparatus made according to claim 1, wherein said porting means includes a tirst set ofV recesses formed in said rotary systems and is traversed by said control pistons to etfect said liquid-buffered Collision event, and wherein a second set of relatively movable recesses formed in said stationary support and in the control pistons eifect said closure and reopening to eiect said inelastic movement and release.

3. Rotary Iapparatus made according to claim 2, wherein the traversal by said control pistons of said irst set of recesses effects gradually varying throttling action and wherein said second setof relatively movable recesses when open produce a maximum of throttling action.

4. Rotary apparatus comprising an assembly of a stationary support for an annular cylinder and at least two cooperating rotary systems having interdigitated power pistons in said cylinder, wherein alternately each system may advance upon the other to effect a gas-buffered collision event between said power pistons and to reach a reverse-locked position, said rotary systems also including intendigitated control pistons in a liquid medium located in a cavity formed by and located between the rotary systems, and fluid porting means arranged between the stationary support, the rotary systems and the control pistons, adapted upon relative movements between the rotary systems relative to each other and the support, rst to produce a liquid-buffered collision event between the control pistons during a Vgas-'buffered collision event between the power pistons, whereby the latter 'event is assisted by the former event in elasticity transferring momentum from one rotary system to the other, second to close whereby the rotary systems move together as a substantially inelastically related pair without momentum transfer, whereby one system is positively replaced by the other in a reverse-locked Iposition, and third to reopen and release one rotary system from its inelastic rel-ationship to the other during an expansion event after said replacement.

5. Rotary apparatus made according to claim 4, wherein said porting means includes elements operative according to the relative rotations of the systems adapted to graduate the driving action of said liquid-buffered collision event from a minimum to a maximum prior to the start of said inelastic relationship.

6. Rotary Iapparatus comprising an assembly of a stationary support for an annular cylinder and -at least two cooperating rotary systems having interdigitated power pistons in said cylinder, reverse-locking means for the respective systems wherein alternately each system may advance lupon the other to eiect a gas-buffered momentum transferring collision event between said power pistons and to interchange reverse-'locked positions of the systems, said rotary systems also including interdigitated control pistons in a liquid medium located in a cavity formed by vand located between the rotary systems, and fluid porting means arranged between-the stationary support, the rotary systems and the control pistons, adapted upon relative movements `between the rotary systems relative to each other and the support, first to produce a liquid-buffered collision event lbetween the control pistons during a gas-buttered collision event Vbetweenthe power pistons, whereby the latter event is assisted by the former event in elastically transferring momentum from one rotary system to the other, second to close whereby the rotary systems move together as a substantially inelastically related pair without momentum transfer, whereby one system is positively replaced by the other in a reverselocked position, and third to reopen to release one rotary system from its inelastic relationship to the other during an expansion event after said replacement, said expansion event with one of said reverse-locking means locking said one system and transferring all momentum to the other.

7. Rotary apparatus made according to claim 6, wherein said porting means includes elements operative according to the relative rotations of the systems adapted increasingly to graduate the eifect of said liquid-buffered collision event upon said gas-buffered collision event.

8. A rotary expansion engine comprising a frame, a power shaft, a toroidal cylinder attached to the frame and surrounding the shaft, a pair of rotors, eachrotor having at least one power. piston in-the cylinder, means forproducing power events between power pistons on the rotors, means adapted alternately to reverse lock the rotors in response to said power events, and driving means between each rotor and the shaft, .said rotors providing between them a circular cavity for hydraulic control lhuid and respectively carrying at least one rotary control piston which is movable relative to the other in said cavity, and fluid porting means arranged between the frame, the rotors and the fronts and backs of the control pistons, adapted first to move toward a closed position during a compression event between 'an advancing and a reverselocked rotor to produce hydraulic resist-ance between them in addition to gaseous compression resistance, whereby the reverse-locked rotor is driven from its Ireverse-locked position yby the advancing rotor, second to close said hydraulic porting means whereby both rotors move together in a substantially hydraulically locked condition until an expansion event is reached after a reverse-locked position is reached by the advancing rotor, and third to open to release the formerly reverse-locked rotor for recession from the reverse-locked position in response to the expansion event reacting against the other rotor at its reverse-locked position.

9. Hydraulic control means for collision processes between abutting relatively moving rotors of alternating piston engines, said rotors being adapted alternately to turn in a stationary frame of said engine; comprising circular recesses in the abutted portions of the rotors together forming a circular cavity adapted to be filled with hydraulic fluid, said frame having separate groups of recesses adjacent said rotors respectively, the recesses in one group alternating in peripheral positions with the recesses in the other group, at least one control lpiston attached to each rotor and having alternating positions and movements within the cavity, at least one recess on each rotor cooperating movably with` a control piston on the other` rotor during alternating piston movements so as intermittently to transfer fluid in the cavity from one side to the other of the cooperating control piston, each Vcontrol piston on each rotor having a passage adapted in response to rotor movements to connect intermittently With successive recesses in one of said groups.

l0. Hydraulic controlpmeans for collision processes between'abutting rotors of alternating piston engines,

said rotors being adapted alternately to turn in a stationary frame of said engine; comprising circular recesses in the abutted portions of the rotors together forming a circular Vcavity adapted to be filled with hydraulic fluid, said frame having groups of recesses in portions adjacent said rotors respectively, the members of each group of recesses alternating in peripheral positions relative to the members of the other group, groups of control pistons attached respectively to the rotors within the cavity, members of each group of control pistons having alternating positions and movements within the cavity with respectpto the members of the other group, groups of 'additional'recesses on each rotor, the members of each additional group alternating in position With respect to the control pistons on the respective rotor, the members of each group of said additional recesses in one rotor cooperating movably with the members of the group of control pistons on the other rotor during alternating rotor movements so as intermittently to transfer uid in the cavity from one side to the other of each control piston, each control piston of each group having passages adapted in response to rotor movements to register intermittently through continuations thereof in the respective rotors with the respective groups of recesses in the frame.

1l. Hydraulic control means for collision processes between abutting rotors of alternating piston engines, said rotors being adapted alternately to turn in a stationary frame of said engine; comprising circular recesses in the abutted portions of the rotors together forming a circular cavity having end walls and adapted to be filled. with hydraulic fluid, said framelhavinggroups of four xed re.- cessesin portions adjacent the outsides of said end Walls respectively, the membersofeachigroup of fixed recesses alternating in peripheral positions relative to the members of the other group, oppositely located pairs of control pistons attached respectively to the rotors, members ofA each pair of control pistons having alternatingspositions and movements within the cavity with respect to the members of the other pair of control pistons, pairs of recesses on each rotor, the members of each pair of control rotor recesses alternating in position with respect t-o the control pistons on the respective rotor, each pair of grooves in one rotor cooperating movably with the pair of control pistons on the other rotor during alternating control piston movements so as intermittently to transfer fluid in the cavity from one side to the other of each control piston, each control piston having passages adapted in response to rot-or movements to register through openings in said end walls with the respective groups of four grooves in the frame.

12. Rotary apparatus comprising an assembly of a stationary support for an annular cylinder and at least two cooperating rotary systems having interdigitated power pistons in said cylinder, wherein alternately each systeml advances upon the other to effect a gas-buttered compression event between said power pistons, control means carried by and respectively movable with the rotary systems, and means adapted to lock said control means together for substantially equal movements thereof. and of;` said rotary systems to which they are attached during a portion of said compression event.

13. Rotary apparatus comprising an assembly of a stationary support for an annular cylinder and at least two cooperating rotary systems having interdigitated'v power pistons in said cylinder, wherein alternately each system elects anadvancing movement upon the -other in'response to' anfexpansion event between certain sets of said power pistons to effect a gas-buttered compression event between other sets ofY said power pistons,- control means carried by andrespectively movable with the rotary systems, locking means adapted to lock said control meansptogetherfor substantially equal movements thereof and of said rotary systems to which they are attached, and timingpmeans responsive to said advancing movements. adapted to actuatesaid locking means during aA portion of said com'- .pression event. p

14. Rotary apparatus comprising an assembly of a stationary support for an annular cylinder and at` least two cooperating rotary systems' having interdigitated power pistons in said cylinder, wherein' alternately each system advancesupon the other to effect agas-buffered compression event between said power pistons, control means comprising control pistons carried by and respectively movable with the rotary systems, hydraulic means adapted to lock said control. pistons together for substantially equal movements thereof and of said rotary systems to which they are attached during a portion ofv said compression event, and hydraulic port means'- timedby the motionsof said rotary systems adapted to actuate-said hydraulicv locking means-V toflock together said control pistons andthe rotaryy systems to'rwhich the controlpistons are attached during a portion/of said compression event; y

l5. Rotary apparatus comprising an assembly of a stationary support for an annular cylinder and at least two cooperatingv rotary systems having interdigitated power pistons in said cylinder, wherein alternately and repeatedly each system advances upon theY other to effect gas-buiered compression events between said power pistons, control means comprising control pistons carried by and respectively movable with the rotary systems, means, adapted to interconnect said control pistons to assumesubstantially equalmovementsthereof and of said rotary systems towhich they are attached, and hydraulic means timed by the motions of said rotary systems adapted to elect inter-connection of said control pistons and therefore of the rotary systems only during a portion of each: of said compression events.

16. Rotary apparatuscomprising an assembly of a stationary supportfor an annular cylinder and at least two cooperating. rotary systems having interdigitatedV power pist-ons in said cylindenwherein alternately each system advances upon the other to elect a gas-buffered compression event between' said power pistons, connective means carried by and respectively movable with the rotary systems, means adapted to connect said connective means for effecting substantially equal movements thereofl and of. said rotary systems to which they are attached during. a portion of said compression event, and means timed by the motions of said rotary systems adapted to elect connection ofV said conectivo means and therefore of the rotary systems during a portion of said compression event. r

17. Hydraulic control means for gaseous collisionprocessesoccurring between cooperating relatively moving rotors of engines of the alternating power piston type; comprising groups of stationary control slots in opposite ends of a space formed by opposite stationary parts of the' engine, relatively movable rotors having rotor members in said space and between them forming a pocket, each rotor member having attached control pistons alter nating with) interdi'gitat'ed control pistons of the other in said pocket and each rotor member having alternating grooves in said pocket cooperating respectively with the control pistons of the other adapted for liquidV transfer lacross the pistons, said control pistons having liquid transfer ports connecting their front and rear faces through said rotor members for timed connections with said stationary slots during rotor movements, adapted to augment said fluid transfer.

References Cited in the tile of this patent UNITED STATES PATENTS 

